Die casting and pressure molding machines



Sept. 24, 1963 J. H. HOERN DIE CASTING AND PRESSURE MOLDING MACHINES 8 Sheets-Sheet 1 Filed Nov. 12, 1959 INVENTOR JOSEPH H. HOERN ATTORNEYS Sept. 24, 1963 J. H. HOERN DIE CASTING AND PRESSURE MOLDING MACHINES Filed Nov. 12, 1959 8 Sheets-Sheet 2 INVENTOR JOSEPH H. HOERN M W/ W ATTORNEYS Sept. 24, 1963 J. H. HOERN DIE CASTING AND PRESSURE MOLDING MACHINES 8 Sheets-Sheet 3 Filed Nov. 12, 1959 ATTORNEYS J. H. HOERN 3,104,433

DIE! CASTING AND PRESSURE MOLDING MACHINES 8 Sheets-Sheet 4 Sept. 24, 1963 Filed Nov. 12, 1959 i R m N N E -n 30 V 6 W m r n 9. H I 5 0m H. u 5% mm H f m 8 S 09 5 5 5 5 w 3 3 mm 9. w. i 00 E I 7L \l m[ \om a! {f c d 3 2. 5 Z mm. 5 02 Q A I C \I on om q am X i 20 mm mm m am 7 1 at o: t nwa uV/ A 1 Eilllfl 2.7 i J mm .4 M b; t 22.225 w mm H -u in m 1 m: 35 mm 18131 I. my vmT mm. N2 32 om. mm 31 8 no mm. hm.

ATTORNEYS BY M J. H. HOERN 3, DIE CASTING AND PRESSURE MOLDING MACHINES 8 Sheets-Sheet 6 1 mw-- w l llll I Q @E l/llllill llzllflwi I; Q 2 t w 11H Ev 1 W I m9 8. 0: 5 E H k m9 8. 6. 5 0:

NO am Sept. 24, 1963 Filed Nov. 12, 1959 INVENTOR JOSEPH H. HOERN C sYfi faw /%@?4 ATTORNEYS Sept. 24, 1963 J. H. HOERN 3,104, 3

DIE CASTING AND PRESSURE MOLDING MACHINES Filed Nov. 12, 1959 8 Sheets-Sheet T k sea ea ,61

INVENTOR JOSEPH H. HOERN F l G. 7 ATTORNEYS Sept. 24, 1963 J. H. HOERN 3,104,433

DIE CASTING AND PRESSURE MOLDING MACHINES Filed Nov. 12, 1959 8 Sheets-Sheet 8 285 C l 9 L x IN VEN TOR. JOSEPH H. HOERN ATTORNEYS United States Patent Office 3 1 Patented Sept. 24, 1 963 3,104,433 DIE CASTING AND PRESSURE MOLDING MACHINES Joseph H. Hoem, 4161 El Monte Dn've, Saginaw, Mich. Filed Nov. 12, 1959, Ser. No. 852,554 15 Claims. (Cl. 22-67) This invention relates to machines for casting molten metal or molding plasticizable material under pressure and more particularly to certain novel and useful improvements in machines of this type.

In recent years machines for forming parts by the compression of metal in a powdered or liquid state in a die at extremely high pressures have been of relatively limited size and to our knowledge no one has designed a machine which could be satisfactorily used to die cast parts as large as cylinder blocks for conventional automobile engines, for instance, on a quantity production basis. A machine suitable for casting large parts of this type on a production schedule would necessarily require extremely large dies which would have to open and close rapidly and move rapidly to remote positions one from another to permit stripping of the part from the dies, while at the same time insuring a positive locking or sealing of the dies during the casting operation to prevent the high pressures employed from spraying the metal out from between the dies. The various toggle-type machines which have been employed to die cast smaller parts are not suitable for forming larger parts since the toggle linkage in each is capable of transferring only relatively limited closing pressures within the limits of the pressure which would snap the link members. Further, the travel of the movable die member is limited in a toggle type machine by the pressures which the linkage is to transmit. Such machines and machines of other design have, in present day practice, provided large, elongate hydraulic cylinders for reciprocating the movable die toward and away from the fixed die member, but with such hydraulic arrangements the length of the stroke is limited by the length of the cylinder and there is also the problem of pump and conduit maintenance. When conventional hydraulic systems are used, the sealing pressure which can be employed is also limited by the elasticity of the conduits or pipes and particularly those which are required to be flexible so that they can connect to the reciprocating platen. The result is that, when the connecting pipes or conduits are subjected to sudden pressures of great force, the elasticity of the pipes will create a die opening at the very time when the die should be tightly sealed, as the shot of metal is being forced into the die mold.

Present machines also use tie bars or tie rods for the purpose of distorting the frame of the machine to allow the dies to come together properly in a manner to provide an equalized pressure on the dies. However, when the machine is a very large machine obviously considerable diliiculty will be involved in distorting its frame to provide a proper alignment of its dies. The present machine has been designed to obviate the disadvantages of conventional machines with a view to the perfection of a machine which can be employed for die casting or pressure molding extremely large parts.

One of the prime objects of the invention is to provide a machine of different concept in which the traveling die can be moved mechanically as rapidly and as far as desired to move the dies into and out of substantially abutting relation, and fluid pressure means is provided in a stationary portion of the machine that can be employed to apply a tremendous die sealing force on the order of 800 tons.

A further object of the invention is to design a machine of the character described in which the many problems encountered with the use of pumps, connecting lines and conduits, and hydraulic cylinders are avoided.

Another object of the invention is to design a machine of the type described which functions to apply a pressure fluid, die sealing force without employing conduit lines leading to a traveling platen which would necessarily limit the force which could be applied and render necessary an externally supported hydraulic system.

A further object of the invention is to design a die casting machine of the character described which need not employ a lubricant such as oil as the pressure fluid medium and accordingly obviates the danger of fire, always present when inflammable fluid and hot metal are in the same vicinity.

Another object of the invention is to provide a machine wherein an equalized die sealing pressure is applied over the die area to maintain the dies in proper alignment and insure that none of the molten material escapes when it is ejected into the die cavity.

A further object of the invention is to provide an improved die casting machine which can operate relatively simply in a sequence in which the various parts move automatically.

Still another object of the invention is to provide a die casting machine or the like of greatly improved design which avoids damage to the casting when the dies are separated and the casting is ejected therefrom.

Other objects and advantages of the invention will be pointed out specifically or will become apparent from the following description when it is considered in conjunction with the appended claims and the accompanying drawings, in which:

FIGURE 1 is a side elevational view of the improved die casting or pressure molding machine with the dies closed and in tightly sealed relation;

FIGURE 2 is a top plan View thereof;

FIGURE 3 is an enlarged, left end, elevational view of the machine shown in FIGURE 1;

FIGURE 4 is a fragmentary, sectional, side elevational view taken on the line 4-4 of FIGURE 3 with the various parts in the positions in which the dies are adjacent and being forced into sealed relation;

FIGURE 5 is a fragmentary, sectional, side elevational view taken on the line 5-5 of FIGURE 3 with the parts in the positions in which they are shown in FIGURE 4;

FIGURE 6 is a fragmentary, sectional plan view taken on the line 6-6 of FIGURE 3 with the parts similarly positioned;

FIGURE 7 is a fragmentary, transverse, sectional view taken on the line 7-7 of FIGURE 5;

FIGURE 8 is a fragmentary, sectional, side elevational view taken on the line 8-3 of FIGURE 7;

FIGURE 9 is a fragmentary, transverse, sectional view taken on the line 9-9 of FIGURE 5;

FIGURE 10 is a fragmentary, sectional, plan view taken on the line 10-10 of FIGURE 9;

FIGURE II is a fragmentary, sectional, top plan view taken on the line 11-11 of FIGURE 4;

FIGURE 12 is an enlarged, fragmentary, side elevational, sectional view with the elements shown in positions in which the traveling platen has moved to retracted position and the dies are open; and

FIGURE 13 is a schematic view illustrating a typical electrical control system for the machine.

Referring now more particularly to the accompanying drawings, in which only a preferred embodiment of the invention is disclosed, a letter F generally indicates the frame of the machine which is particularly designed to avoid the use of a heavy and bulky bed or base of the type which previous die casting machines have employed. Support block members 10 are spaced longitudinally and transversely, as shown in FIGURES 1 and 3, to function as corner posts and are arranged to support a rear end plate 11 and a front end plate 12. Bolts 13 (FIGURE 3) may be employed to secure the end plates 11 and 12 in position on the corner blocks and side plate members 14, which are recessed as at 15 to receive the end plate members 11 and 12, can be suitably secured to the end plate members by bolts 16. The support blocks 10, end members 11 and 12, and side plate members 14 which may be perforated as at 14a and 14b to provide access to the interior, comprise a rigid, stationary frame section for supporting a die casting machine which is designed to exert a pressure in the neighborhood of 800 tons.

Mounted on the rear plate 11 by bolts 17 and spaced from the plate 11 by spacer sleeves 18 is a stationary, rear support plate 19 designed to cooperate with the plate 11 in supporting final or die closing pressure applying means in a manner which will be later described. The plate 19 also supports drive elements for operating the final or closing pressure elements and for rapid traversing the movable die platen 20 forwardly and rearwardly to and from a position in which the movable die member 21 thereon is in a forward position adjacent the stationary die member 22. As has been previously noted, the instant die casting machine avoids the use of an elongate hydraulic cylinder for moving the traveling platen 20 to and from the position in which the final closing pressure is applied. Instead, a mechanical rapid traversing arrangement is employed in conjunction with die closing pressure exerting members which obviates many of the difficulties encountered with so-called hydraulic machines.

The Rapid Traversing Mechanism Mounted on the plate 19 (see FIGURE 5) is a tapered roller bearing 23 having a flanged casing 24 fixed in position on the plate 19 by bolts 25. Within the bearing 23, tapered rollers 26 supported between outer race members 27 and an inner race member 28, as shown, journal an elongate, rotatable shaft 29. A head plate or hearing cap 30 bolts to the casing 24 as at 31 and seals off the bearing 23. Keyed to the outer end of the rotatable shaft 29, as at 32, is a pulley 33 which is driven by a belt 34 trained around a pulley 35 on the armature shaft 36 of a motor 37.

Tubular shaft or sleeve 29 extends through an opening 38 in the plate 19 and through an opening 39 in the plate 11 and a roller bearing 40 is provided, as shown, to support the front end of the shaft 29. Bearing 46 comprises an outer race member 41, roller bearings 42, and an inner race member 43 secured in position by a head plate or bearing cap 44 with bolts 45 or in any suitable manner. At its front end the bore of the shaft 29 is enlarged and threaded as at 46 to receive a ball screw nut assembly generally designated 47 of the type used in steering gear assemblies. The recirculating balls 48 of the conventional ball nut assembly are shown at 48 and the cooperating ball screw 49 is shown as axially received by a member 50 mounted on the traveling platen 20. It will be seen that the member 50 comprises a base plate 51, having a section fitting into a central opening 52 in the traveling platen 20. Bolts 53 secure the plate 51 and a flanged end member 54. The end of the screw 49 is provided with a pair of opposed, horizontally extending notches or grooves 55 which receive the flanges 56, provided on the plate 53. The flanges 56 prevent axial rotation of the screw 49, however, it will be seen that they are of lesser thickness axially than the width of grooves 55, so that the traveling platen 20 can have a slight relative axial movement in the member 5t). This clearance 56a, which may amount to l 1o of an inch, will permit the traveling platen 20 to move forwardly the required distance when the closing pressure is applied.

The Die Closing Mechanism Extending rearwardly from the traveling platen 20,

and rigidly fixed thereto, are radially disposed, thrust rod members 57 which are arranged radially equidistant from the central screw 49 on the platen 20 in uniformly spaced, circumferential relation, so that a relatively uniform closing pressure may be applied. The final closing force of 800 tons is applied to the thrust rods 57, which are secured to the tnaveling platen 20 by bolts 58 (FIGURE 4) through similarly arranged piston assemblies generally designated 59 supported by the plates 11 and 19 in axial alignment with the thrust rods 57 (see FIG- URE 4). The piston assemblies 59, which are received in cylinders 60 secured to the plate 19 by screws 61, include heads 62, return spring retainer plates 63, and sleeve members 64, which are threaded as at 65 to ad justably receive the cooperatively threaded, pressure applying sleeve members 66. The piston head members 62 are open as at 62a so that the position of the members 66, which have enlarged heads, as shown, may be axially adjusted and the stroke of the piston units 59 varied to suit the particular dies being used. Further, members 66 are bored as at 66a so that they can receive thrust rods 57 (see FIGURE 12) during the retraction stroke of the platen 20 when blocking members 67 are moved from between the sleeves 66 and shafts 57, as shown in FIGURE 12. The blocks 67 are automatically positioned between the members 66 and shafts 57, just prior to applying the closing pressure, and are raised prior to the retract stroke of the traveling platen 20 so that the thrust rods 57 may enter the sleeve 66 in a manner which will be presently described. The adjustment of sleeves 66 is accomplished through a chain 68, as shown in FIGURES 4 and 7, which is trained around sprocket members 69 fixed on the sleeve members 64. The sleeves 64 at their opposite ends have flanged portions 64a, received between the rear face of the piston head members 62, and an internal shoulder 70 formed in each spring retainer member 63 so that the members are substantially axially restrained and rotation of members 64 will adjust the members 66 axially.

As shown in FIGURES 7 and 8, adjustment of the members 66 can be a manual operation, the plate 11 having mounted thereon a sprocket member 71 having a hexagonal head portion 72, which may be gripped by a wrench. A threaded pin 73 can be provided to secure the sprockets 71 on the plate 11 and access to the sprocket 71 may be had through one of the openings 14a in the side plates 14.

Provided in the circumferentially spaced openings 74 in the members 63 are springs 75, which return the piston assemblies 59 when the closing pressure is released. It will be seen that the spaces necessary for die closing travel are provided between the shoulder on each piston head 62 and stop plates 78 which are bolted to the cylinder members 60, as at 79. It is important to note that the iston assemblies 57 do not reciprocate with the traveling platen 20, but rather are, in effect, a portion of the frame. The plate 19, in fact, forms the head of each cylinder 60 and each has an axially directed passage portion 80 leading to the interior 81 of the cylinder, as shown in FIGURE 4. The piston assemblies 59 are moved forwardly in a manner which will be presently described, only when the ball screw 49 has rapid traversed the traveling platen 20 forwardly to a position in which the dies 21 and 22 are substantially adjacent or contiguous.

Supported from the frame plates 19 and 11 is a motor support plate 82, which supports not only motor 37 but a motor 83 as well. Sleeve members 84 fixed by bolts 85 extending into the top of plate 11 may be provided on the plate 11, as shown in FIGURES 1 and 3, to assist in supporting the plate 82. The motor 83 is connected to drive a shaft 86 through the medium of a belt 87 trained around a pulley 88 on the armature shaft 89 of motor 83 and a pulley 90 keyed on shaft 86. As shown in FIGURE 4, the shaft 86 to which pulley 90 is keyed is tubular and is rotatably supported on a stub shaft 91, which carries roller bearings 92 and 93. Roller bearings 92 and 93 comprise inner race members 92a and 93a, outer race members 92b and 93b, and balls 92c and 936, respectively. The stub shaft 91 has an inner end 91a received within a bore 94 provided for it in the frame wall 19. Spur gear teeth 95 are provided on the shaft 86 and, as shown in FlGURE 6, are in meshed driving relationship with a pair of gears 96 and 97 which are fixed on bail screw shafts 98 and 99, respectively.

Bearing support members 180, fixed in openings 1G1 provided for them in the wall 19, support tapered roller bearings generally designated 102 within which gear hub portions 96a and 97:: are rotatably received and roller bearings 103 are provided to revolvably support the outer ends of ball shafts 98 and 99. Roller bearing 103 comprises inner race members 1630, outer race members 103b, and bull 1039. The tapered roller bearings 102 include outer race members 194, rollers 105, and inner race members 106. The bearing support members 199 are secured to the wall 19 by bolts or screws 107. Gears 96 and 97 are keyed to their respective shafts 9S and 99 as at 108 and the ends of shafts 98 and 99 are threaded as at 109, so that nuts 11.0 may be employed to secure the gears 96 and 97 in position on the shafts 98 and 99, respectively.

Traveling ball nut assemblies of conventional design generally designated 111 are provided on the screw shafts 98 and 99 and support a yoke or actuator plate 112 which applies the die closing pressure in a manner now to be described. The assemblies 111 comprise nut members 113 with recirculating balls 114 and are secured to the plate 112 by screws 115. Yoke member 112 has openings 117 for freely passing the screw shafts 98 and 99 and since the front ends of shafts 98 and 99 are received in thrust bearings 118 provided in a plate 119 which is fixed on the frame F, it will be plain that, upon rotation of the axially fixed screw shafts 98 and 99, the nut members 113 and yoke 112 will move axially.

FIGURES 4 and 6 show the cylinder 120 which is fixed to the wall 19 by a shouldered plate 121, in any suitable manner, as by using bolts or screws 122. The reciprocable connecting plate 112 mounts a guide sleeve 123 having an end wall 124 by suitable screws or bolts 125 and, as will be noted, the sleeve 123 telescopically receives the cylinder 120. Cylinder 120 houses a piston assembly 126 which dispenses fluid under pressure to the cylinder 60 from the fluid supply chamber 127 closed by the piston assembly 126 to apply the closing pressure of some 800 tons. A passage 128 communicates with the cylinders 60 through a transversely disposed passage 129, vertically inclined passages 139 (FIGURE 3), vertical passages 131, and the passages 80.

The mechanical advantage obtained through use of the relatively small piston 126 which displaces the considerably larger diameter pistons 59 is an important factor since it is desired that the pressure exerted by each of the piston assemblies 59 be in the neighborhood of 200 tons. The communicating passage system provided solely in place 19 and leading from the chamber 127 will always be completely filled with the incompressible fluid used, which suitably may be a liquid silicone. It is desirable that the fluid used be incompressible, noninfiammable, and nonabrasive in character.

The piston assembly 127 is bored, as at 132, to receive a guide pin 133 having scmispherical ends 134 and 135, as shown. The conical end walls 136 and 137 which receive the ends 134 and 135, respectively, are formed in the piston 126, as shown, and in the cross head or connecting plate 112 which receives the other end of guide pin 133, and with this construction misalignment of the parts is ellectively prevented. The guide pin 135 has a flange 133a received within an enlarged portion 132a of the bore 132, a ring 138 being provided fixed to the piston 126 to maintain this connection of the guide 6 pin and piston 126. It will be noted that the diameter of the flange 133a is less than the internal diameter of the enlarged portion 132a of the piston, so that some tilting of pin 135 can occur without binding.

Flainly, when the piston 126 is moved toward wall 19 by the cross head 112, a closing pressure is applied to the piston assemblies 59 and conversely when the piston 126 is moved outwardly in the cylinder 120 the springs 75 return the piston assemblies 59 and piston 126 to original position.

As has been noted, the traveling platen 20 carries the movable die member 21. Both motors 37 and 83, through the intermediary mechanism which has been described, operate to control the movement of the platen 20. The motor 37 operating through the screw shaft 49 moves the platen 20 from a distance considerably removed from the fixed die 22 to a position in which dies 21 and 22 are substantially abutting and the motor 83, thence, through piston assemblies 59 applies the considerable closing pressure which moves the die 21 the very short additional distance into clamped engagement with the fixed die 22. No tie rods are necessary in the instant machine since it is not necessary to distort the frame to allow for any misalignment of the dies 21 and 22. Rather, the 800 ton force which is necessary, not to move the dies 21 and 22 into engagement but to retain them in sealed engagement when the die cast metal is injected into the die cavity, is applied at uniformly spaced apart areas of the platen 21}.

As shown in FIGURES 2 and 3, particularly, the platen 20 is supported for reciprocating travel by the frame side plates 14 to which T-shapcd guides 139 are fixed by suitable screws or bolts 140. Rail members 141 secured on the T-shaped guides 139, as with screws or bolts 142, cooperate with the members 139 to define channel-shaped guides 143 which receive the slide members 144 which are fixed to the upper end of the traveling platen 28 by bolt members 145. The plate 119, which cooperates with plate 19 to support the screw shafts 98 and 99, is fixed to block members 146 which are bolted, as at 147, to the top rail members 141. The arrangement described wherein the guides or ways are, in effect, provided in the side walls of the frame to support the traveling platen 20 in its reciprocation toward and away from the fixed die member 22, provides a construction which is believed greatly superior to die casting machines of conventional construction employing tie rods on which the traveling platen slides.

It has previously been mentioned that, when the traveling platen 20 is in rearward or outward position, the thrust rods or shafts 5 7 are received within the piston members 66. When the traveling platen 20 is moved forwardly by the screw shaft 49 to a position in which die 21 is about "3 of an inch from die 22 the piston members 66 and thrust rods 57 will be spaced from one another a predetermined distance. In order that pressure may be exerted on the thrust rods 57 by the piston members 66, the block members 67 are moved from a position outward of the bores 66:: in members 66, as shown in FIGURE 12, to a position sandwiched between the members 66 and 57, as shown in FIGURE 4. This movement of the blocks 67 occurs in a manner which will now be explained when the platen 20 has been moved forwardly by the screw 49 and the thrust rods 57 are sufficiently forwardly to permit entrance of the blocks 67 between the rods 57 and members 66. A plate 148 mounting the ejector rods 149 which extend through passages 150 in the platen 20 and 151 in the die member 21 is provided between the side frame members or plates 14 between the fixed end plate member or abutment wall 11 and the reciprocating platen 20, as shown in FlGURES 4, 5, and 9. The front ends of piston members 66, which are of enlarged diameter as shown in FIGURE 10, are formed with vertically disposed grooves or passages 152 therein, for admitting the blocks 67. Each member 66 has a pair of side flanges 66b against which clamping members 153 bear to secure the piston member 66 to the plate 148, suitable screws or bolts 154 connecting the members 153 and plate 148 and thereby the piston members 66 and plate 148 for longitudinal movement, as shown. The plates 67 are of such thickness, relative to the length of the portions 152, as to provide the necessary clearance for movement of blocks 67.

Plate 148 has an opening 156 freely passing the nut member 47 and openings 157 which freely pass the thrust rods 57. The blocks 67 are connected at each side by vertically extending, rigid straps 158, as shown in FIGURES 9 and l0, the straps 158 being suitably secured to the blocks 67 by rivets or the like 159. The straps 158 at the right side of plate 148 in FIGURE 9 extend above the upper block member 67 and are connected by a bar 160, as shown. Lugs 161 provided on the bar 160 and on the top of the uppermost block 67 at the left :side of plate 148 in FIGURE 9 connect to link members 162 which suspend the system from an actuator member 163 which is automatically operated upon movement of the yoke 112 to operate piston assemblies 59 in a manner which will be later described. The links 162 are pivotally connected to the lugs 161 and extending arms 163a of the actuator 163 by pins 164, as shown. As indicated in FIGURES and 9, the actuator member 163 is pivotally mounted on plate 143 as at 164 and has a spherical shaped, upper end 165 received, as shown, within a clevis 166 (FIGURES 9 and 11) on the one end of a rod member 167. In FIGURE 9 the actuator 163 is disposed such that blocks 67 are in alignment with thrust rods 57 in a position to permit the piston members 66 to apply pressure to the rods 57. If the actuator member 163 is oppositely tilted, however, about its pivot 164, the left hand blocks 67 (FIGURE 9) will be raised to the position in which they are shown in FIGURE 12, out of the path of thrust rods 57 and the right hand blocks 67 will be lowered the same distance so that they also are out of the path of thrust rods 57. Retracting movement of the yoke 112, which adjusts the position of the actuator 163 to move the blocks 67 out of the path of the thrust rods 57, will free the bores 66:; of piston members 66 for entry of the rods 57 on the retraction stroke of platen 20.

The mechanism for automatically operating the actuator 163 will be next described, and attention is di reoted particularly to FIGURES 4, 9, and ll for a disclosure thereof. The fixed wall 19 mounts a fixed clevis 168 under cylinder 126 and a clevis pin 169 supports a sleeve 170 for swinging movement in a horizontal plane. Fixed on the member 170 which is provided with a front bearing 170a is a cam or track member generally designated 171 and having a trackway 172 with an angularly directed portion 172a. Front and rear clamp members 173 are employed to fix the track member 171 in position on the tube 170. Mounted on the underside of cross head or connecting yoke member 112 by bolts or screws 174 is a plate 175 carrying a dependent roller 176 which rides in the cam track 172. The tubular member 170 telescopically receives the rod 167 and when the roller 176 reaches the portion 172a of the track 172 it will necessarily pivot the sleeve 170 and rod 167 about the pin 169. This, of course, has the effect of changing the position of the actuator 163 about its central pivot point 164. The plate 177, which is mounted on the upper edge of the plate 148 by screws 178 or the like, supports the outer end of the rod 167 and is slotted as at 179 to permit free movement of the upper end of the actuator member 163. If the position of piston members 66 is adjusted axially relative to member 64, as in a case where a die 21 or 22 having a different thickness is being substituted for the die in the machine, the rod 167 is free to move axially in the tube or sleeve 170 to adjust to the new position.

The die members 21 and 22 are releasably secured to the movable platen 20 and fixed platen or frame member 12 in any suitable manner. In the drawings, T- slots 188 are shown as provided in the members 20 and 12 to receive T nuts 181 which are threaded on screws 182 carried by the die members. In the case of the die 21, the die face is provided with enlarged openings 183 at points peripherally spaced from the die cavity 184 to receive the heads 185 of screws 182. The T slots which are not used in the drawings may be employed with othcr dies providing that the openings 182a leading through the die members 21 and 22 are outside and spaced from the die cavity 184. As previously noted, the ejector rods 149 are carried by plate 143 and extend through to a position in which they are flush with the surface of the die cavity 184. During the retract stroke of platen 20 when the piston members 66 are moved rearwardly initially by the piston return springs 75, the ejector pins 149 will move the slight distance rearwardly with them. However, when the platen 20 is rapid traversed rearwardly by the screw shaft 49 the pins 149 will operate to strip the casting from the mold cavity so that it is free to fail to a suitable conveyor or the like positioned under the machine. Since the machine is supported on blocks it) at its corners only, ample space is provided so that an endless conveyor may extend under the machine to convey the castings which are formed in the machine on a quantity production schedule. When the position of piston members 66 is being adjusted and the screws 154 holding clamp plate 153 are backed off slightly to permit rotation of the piston members 66, the pins 186 projecting outwardly from plate 148 assist in supporting the plate 148 in position.

The Shot Injection System The charge of metal is applied to the die cavity 184 in a novel manner disclosed in applicant's co-pending application Serial No. 66,452. Preferably, as previously noted, a shot injection plunger 187 is employed which moves at a relatively slow rate of speed initially to close off a material supply spout, thence at a grcat rate of speed, and with tremendous force, to move the molten metal or the like into the die cavity 184, and finally at a relatively reduced rate of speed while retracting to original position. A longitudinally disposed, rectilinear housing 188 supported at one end by the wall 12 and at the other end by an upright housing or casing 189 is provided to house the shot plunger 187 which has an enlarged end 187a and is adapted to extend through an opening or cold chamber 190 in fixed die 22 and an aligned opening or cold chamber 191 through wall 12. The housing 188, which includes side walls 192 and a partial top wall 193, has integral side flanges 194 so that it can be secured to the end wall 12 by bolt members 195.

It will be seen that the passages 190 and 191 are of the diameter of the enlarged head 1870 of the injection rod or plunger 187 and mounted on the rear wall 12 is a member 196 having a bore 197 of the same diameter as openings 190 and 191. A pouring spout 198 leads through the member 196 from the exterior thereof to the bore 197 and, if it be assumed that the top wall 193 terminates short of the wall 12, then the pouring spout 198 is exposed so that it may be manually or mechanically charged with the material to be formed in the dies.

The Control System and Operation At the beginning of the cycle when platen 20 and retractable die 21 are in rearward or retracted position and rack 201 and slide 199 are also in retracted position, the operator, in putting the system into operation, first of all must start the rapid traverse motor 37 and this can be done by depressing a push button 285 (FIGURE 13) to start the operation of the control system. The control system which will be described may be varied considerably so that the operation of the machine is entirely automatic or may be made somewhat semi-automatic so that the machine is at least partially under the control of an operator. The instant system which employs timing cams is shown for the sake of simplicity of illustration and pictures the system as ready to begin a cycle of operation. When button 285 is depressed to energize conduit c, the geared down timer motor 286 is started and continues to revolve its timer cams in the usual manner through a complete revolution during which time one cycle of the machine is completed. The cams may be mounted on an extension of the motor shaft adjacent the switches they are to operate, in the usual manner. When timer 286 is started, cam 287 moves counterclockwisely, as do all the timer cams, to close normally open switch 288 in circuit d and motor 37 is energized to revolve shaft 29. Nut 47, through shaft 49, moves platen 20 forwardly and when movable die 21 is approximately ,5 of an inch from stationary die 22 the cam 287 permits switch 288 to open. At the same time, cam 289 closes normally open switch 290 in circuit line f and circuit line I is closed to start motor 83. Energization of motor 83, as has been noted, revolves screw shafts 98 and 99 through pulley 88, shaft 86, and gears 95, 96, and 97, and since shafts 98 and 99 are fixed in position axially, nuts I13 move the yoke 112 toward the wall 19 to the left, as shown in FIGURE 6, which forces fluid under pressure through the passage system 128, 129, 130, and 131 to the ports 80 entering cylinders 60.

During the time that piston 126 is moving toward the left (FIGURE 4) in cylinder 129. the arm 175 carrying roller 176, which is secured to yoke plate 112, is moving toward the left in the track 172, The thrust rods 57, having been moved forwardly by the screw 49, are clear of the bores 66a in the piston member 66 sufficiently to permit the introduction of plates 67. At the outset of the closing movement of piston 126 and yoke 112, the roller 176 is in the portion 172a of the trackw-ay 172 and trackway 171, sleeve 170, and clevis rod 167 will accordingly almost initially be pivoted about pin 169 to pivot actuator plate 163 about pivot 164 to the position shown in FIGURE 9 and move blocks 67 vertically into place between the piston member 66 and thrust rods 57. Accordingly, as the piston assemblies 59 are forced forwardly and move the die 21 into engagement with the fixed die 22, the force of 890 tons is exerted on the platen 20 through piston members 66, blocks 67, and the thrust rods 57.

The timer cam 290 holds the dies 21 and 22 in closed position for a predetermined period of time, after which it permits switch 290 to open again. After the material has been injected into the die cavity in a manner to be described and the part formed has had sufiicient time to cool, the reversing circuit g of motor 93 will be energized to drive motor 83 in a reverse direction and move piston 126 outwardly so that springs 75 will return piston assemblies 59. This is accomplished by the cam 291 closing normally open switch 292 at the time switch 290 is permitted to open. When piston assemblies 59 have returned to retracted position, normally open switch 293 in the reversing circuit e of motor 37 is energized by cam 294 which closes normally open switch 295, and motor 37 is driven reversely to retract screw 49 and platen 2G to out position once again.

During the retracting movement of piston 126 the arm 17S and roller 176 are moved in the same direction and clevis rod 167 is returned to pivot actuator plate 163 about pivot 164 and move the blocks 67 vertically out of sandwiched position between piston members 66 and thrust rods 57. Accordingly, When motor 37 is driven in the reverse direction to retract the platen 20, the thrust rods 57 will be received within the bores 66a of members 66 in the manner demonstrated in FIGURE 12. As the platen 20 and movable die 21 retract, the

10 ejector rods 149 will, of course, operate to separate the casting from the die cavity 184.

It is to be understood that the drawings and descriptive matter are in all cases to be interpreted as merely illustrative of the principles of the invention, rather than as limiting the same in any way, since it is contemplated that various changes may be made in the various elements to achieve like results without departing from the spirit of the invention or the scope of the ap pended claims.

I claim:

1. In a die casting or molding machine; frame means including a fixed wall section; a die normally fixed on said frame means at a spaced distance from said wall section; a movable die assembly between said Wall section and die supported by said frame means for reciprocating movement therebetween; means including a rotatable part and a generally reciprocable part connected to travel said movable die assembly rapidly toward and away from said normally fixed die; lost motion coupling means connecting said last means with the said movable die assembly permitting said movable die assembly a closing increment of movement; means for supplying said fixed die with the material to be formed; a plurality of generally radially arranged member carried by said Wall section for applying a uniform closing pressure to said movable die assembly and moving it a closing increment toward said normally fixed die; and fluid pressure means for applying a closing force to said radially arranged members independently of said means connected to travel the movable die assembly.

2. The combination defined in claim 1 in which said movable die assembly includes a platen and said frame means includes side plates; and cooperating way and guide means on said platen and side plates along the top of said side plates.

3. The combination defined in claim 1 in which said rotatable part and generally reciprocable part comprise a ball nut and screw assembly.

4. The combination defined in claim 1 in which said movable die assembly has rearwardly extending parts in alignment with said radially arranged members; said radially arranged members comprise pressure fluid carrying members having forwardly displaceable portions; said wall section having a fluid filled reservoir system communicating with said pressure fluid carrying members; a piston in said reservoir for displacing the fluid therein and displacing said portions; and an electric motor, and rapid traverse motion transmission means connecting said piston and motor for moving said piston to effect a seal of said movable die assembly and die, and to release them from sealed relation.

5. The combination defined in claim 1 in which said radially arranged members are elongate .and have longitudinal bores therein; said movable die assembly has rearwardly extending thrust members receivable in the bores; and means is actuated, when the said thrust members are forwardly spaced from said bores and the movable die assembly and die are substantially in abutting relation, to move between said bores and thrust members to prevent retrograde movement of said movable die assembly under the pressure of the material to be formed.

6. The combination defined in claim 1 in which the radially arranged members are relatively axially adjustable and comprise outer piston members and inner piston members; and means connecting said axially adjustable members for movement in unison.

7. In a die casting or molding machine; a die frame means; movable die means travelable to and fro on said frame means; means for injecting a material to be formed to said die and die means; rapid traversing means for traveling said movable die means from a remote position to said die; at least one axially displaceable pressure fluid actuated member mounted by said frame means for movement toward and away from said die and having an opening therein; a thrust member extending from said movable die means and receivable in said opening; blocking means actuatable to move between the opening in said axially displaceable member and said thrust member to prevent retrograde movement of said die means when material is injected to said die means and die a fluid pressure reservoir on said frame means; a mechanical advantage exerting, fluid displacement member movable to and fro therein; said frame means having passage means freely connecting said fluid actuated member with said reservoir; and means for actuating said displacement member independently of said rapid traversing means at a time when said reservoir, passage means, and pressure fluid actuated member are freely communicating and applying a die sealing pressure to said blocking means and thrust member.

8. The combination defined in claim 7 in which said reservoir is a cylinder and said displacement member a piston therein; and said means for actuating said displacement member includes a yoke connected with the said piston, and a ball nut and screw assembly for moving the yoke.

9. The combination defined in claim 8 in which a cam track and follower assembly actuated by said yoke moves said blocking means.

10. The combination defined in claim 8 in which ejector rods are carried by said frame means and openings provided in said movable die means freely pass said rods.

11. In a die casting or molding machine; frame means; relatively movable die members thereon movable toward and away from one another; said frame mean-s including a stationary frame section; means for rapid traversing one of said die members toward and away from the other die member; means for supplying said die members with the material to be formed; at least one force applying member carried by said frame section for applying a final pressure operative to seal said die members in clamped relation; port means formed within said stationary frame section including a passage leading directly to the force applying member; a fluid pressure reservoir on said stationary frame section communicating freely with said port means; a mechanical advantage exerting, fluid displacement member travelable to and fro in said reservoir; and means for driving said fluid displacement member when said reservoir, port means, and passage are freely communicating for applying a fluid pressure force to said force applying member.

12. In a die casting or molding machine; frame means; relatively movable die members thereon movable toward and away from one another; means for rapid traversing one of said die members toward and away from the other die member; means for supplying said die members with the material to be formed; at least one force applying member carried by said frame section for moving said movable die member a final increment toward the other die member and applying a final pressure operative to seal said die members in clamped relation; lost motion coupling means connecting said rapid traversing means with said movable die member permitting said movable die member a closing increment of movement; a fluid pressure reservoir communicating with said force applying member; a fluid displacement member for said reservoir; and means for driving said fluid displacement member independently of said rapid traversing means for applying a force to said force applying member.

13. In a die casting or molding machine; frame means; relatively movable die members thereon movable toward and away from one another; means, including a driven and driving mechanical part, connected with one of said die members for rapid traversing said one of said die members toward and away from the other die member; means for supplying said die members with the material to be formed; at least one force applying member carried by said frame section for moving said movable die member a final increment toward the other die member and applying a final pressure independently of said driven and driving mechanical part operative to seal said die members in clamped relation; said rapid travers ing means including further a lost motion connection with said movable die member permitting said movable die member a sealing increment of movement; a fluid pressure reservoir communicating with said force applying member; a fluid displacement member for said reservoir; and means for driving said fluid displacement member for applying a force to said force applying member.

14. In a die casting or molding machine; frame means; relatively movable die members thereon movable toward and away from one another; means, including a screw shaft connected with one of said die members for rapid traversing said one of said die members toward and away from the other die member; nut means for reciprocating said shaft; means for supplying said die mem bers with the material to be formed; at least one force applying member, carried by said frame section outward of said shaft for moving said movable die member a final increment toward the other die member and applying a final pressure independently of said shaft, operative to seal said die members in clamped relation; said shaft having a lost motion connection with said movable die member permitting said movable die member a sealing increment of movement; a fluid pressure reservoir com municating with said force applying member; a fluid displacement member for said reservoir; and means for driving said fluid displacement member for applying a force to said force applying member.

15. In a die casting or molding machine; frame means; die members thereon including a die movable toward and away from another die; means for rapid traversing the movable die member toward and away from the other die member; means for supplying said die members with the material to be formed; said rapid traversing means having a lost motion connection with said movable die member permitting said movable die member a sealing increment of movement toward the other die; and fluid pressure means for applying a closing force to said movable die member independently of movement of said means connected to rapid traverse the movable die assembly.

References Cited in the file of this patent UNITED STATES PATENTS 2,166,106 Gormley July 18, 1939 2,484,344 Hiller et al. Oct. ll, 1949 2,564,885 Sternberg Aug. 21, 1951 2,848,771 Eggenberger Aug. 26, 1958 2,869,190 Schofield Jan. 20, 1959 2,887,742 Stern May 26, 1959 2,893,082 Hodler July 7, 1959 :5 She s ts-Sheet 1 UNITED STATES PATENT OFFICE Certificate of Correction Patent No. 3,104,433 September 2), H163 Joseph H. IIoern an; in the above numbered patent requiring correction and It is hereby certified that error zip e that the said Letters Patent should rem as c-orrvvtml lwlon'.

first sheet containing columns 9, 1f), 11 and 12, and insert In the grant (only), $1 rike out the instead columns 5, 6,7 and 811:; shown below Signed and sealed this 12th day of May 196- [SEAL] EDWARD J. BRENNER,

Attest:

ERNEST V. SYVIDER,

C'ommz'mioncr of Parents.

3 Sheets-Sheet. 2

is tubular and is rotatably supported on a stub shaft 91, which carries roller bearings 92 and 93. Roller bearings 92 and 93 comprise inner race members 92a and 93a, outer race members 92b and 93b, and balls 92c and 930, respectively. The stub shaft 91 has an inner end 91a received within a bore 94 provided for it in the frame wall 19. Spur gear teeth 95 are provided on the shaft 86 and, as shown in FIGURE 6, are in meshed driving relationship with a pair of gears 96 and 97 which are fixed on bail screw shafts 98 and 99, respectively.

Bearing support members 100, fixed in openings 101 provided for them in the wall 19, support tapered roller bearings generally designated 102 within which gear hub portions 96a and 97:: are rotatably received and roller bearings 103 are provided to revolvably support the outer ends of ball shafts 98 and 99. Roller bearing 103 com prises inner race members 103a, outer race members 103b, and ball 103c. The tapered roller bearings 102 include outer race members 104, rollers 105, and inner race members 106. The bearing support members are secured to the wall 19 by bolts or screws 107. Gears 96 and 97 are keyed to their respective shafts 98 and 99 as at 108 and the ends of shafts 98 and 99 are threaded as at 109, so that nuts 110 may be employed to secure the gears 96 and 97 in position on the shafts 98 and 99, respectively.

Traveling ball nut assemblies of conventional design generally designated 111 are provided on the screw shafts 98 and 99 and support a yoke or actuator plate 112 which applies the die closing pressure in a manner now to be described. The assemblies 111 comprise nut members 113 with recirculating balls 114 and are secured to the plate 112 by screws 115. Yoke member 112 has openings 117 for freely passing the screw shafts 98 and 99 and since the front ends of shafts 98 and 99 are received in thrust bearings 118 provided in a plate 119 which is fixed on the frame F, it will be plain that, upon rotation of the axially fixed screw shafts 98 and 99, the not members 113 and yoke 112 will move axially.

FIGURES 4 and 6 show the cylinder 120 which is fixed to the wall 19 by a shouldered plate 121, in any suitable manner, as by using bolts or screws 122. The reciprocable connecting plate 112 mounts a guide sleeve 123 having an end wall 124 by suitable screws or bolm 125 and, as will be noted, the sleeve 123 telescopically receives the cylinder 120. Cylinder 120 houses a piston assembly 126 which dispenses fluid under pressure to the cylinders 60 from the fluid supply chamber 127 closed by the piston assembly 126 to apply the closing pressure of some 800 tons. A passage 123 communicates with the cylinders 60 through a transversely disposed passage 129, vertically inclined passages 130 (FIGURE 3), vertical passages 13], and the passages 80.

The mechanical advantage obtained through use of the relatively small piston 12 which displaces the considerably larger diameter pistons 59 is an important factor since it is desired that the pressure exerted by each of the piston assemblies 59 be in the neighborhood of 200 tons. The communicating passage system provided solely in place 19 and leading from the chamber 127 will always be completely filled with the incompressible fluid used, which suitably may be a liquid silicone. It is desirable that the fluid used be incompressible, noninflammable, and nonabrasive in character.

The piston assembly 127 is bored, as at 132, to receive a guide pin 133 having semispherical ends 134 and 135, as shown. The conical end walls 136 and 137 which receive the ends 134 and 135, respectively, are formed in the piston 126, as shown, and in the cross head or connecting plate 112 which receives the other end of guide pin 133, and with this construction misalignment of the parts is effectively prevented. The guide pin has a flange 133:: received within an enlarged portion 132a of the bore 132, a ring 138 being provided fixed to the piston 126 to maintain this connection of the guide pin 135 and piston 126. It Will he noted that the diameter of the flange 133a is less than the internal diameter of the enlarged portion 1324 of the piston, so that some tilting of pin 135 can occur without binding.

Plainly, when the piston 126 is moved toward wall 19 by the cross head 112, a closing pressure is applied to the piston assemblies 59 and conversely when the piston 126 is moved outwardly in the cylinder 120 the springs 75 return the piston assemblies 59 and piston 126 to original position.

As has been noted the traveling platen 20 carries the movable die member 21. Both motors 37 and 83, through the intermediary mechanism which has been described, operate to control the movement of the platen 20. The motor 37 operating through the screw shaft 49 moves the platen 20 from a distance considerably removed from the fixed die 22 to a position in which dies 21 and 22 are substantially abutting and the motor 83, thence, through piston assemblies 59 applies the con siderable closing pressure which moves the die 21 the very short additional distance into clamped engagement with the fixed die 22. No tie rods are necessary in the instant machine since it is not necessary to distort the frame to allow for any misalignment of the dies 21 and 22. Rather, the 800 ton force which is necessary, not to move the dies 21 and 22 into engagement but to retain them in sealed engagement when the die cast metal is injected into the die cavity, is applied at uniformly spaced apart areas of the platen 20.

As shown in FIGURES 2 and 3, particularly, the platen 29 is supported for reciprocating travel by the frame side plates 14 to which T-shaped guides 139 are fixed by suitable screws or bolts 140. Rail members 141 secured on the l"-shaper.l guides 139, as with screws or bolts 142, cooperate with the members 139 to define channel-shaped guides 143 which receive the slide members 144 which are fixed to the upper end of the traveling platen 20 by bolt members 145. The plate 119, which cooperates with plate 19 to support the screw shafts 9S and 99, is fixed to block members 146 which are bolted, as at 147, to the top rail members 141. The arrangcment described wherein the guides or ways are, in effect, provided in the side walls of the frame to support the traveling platen 20 in its reciprocation toward and away from the fixed die member 22, provides a construction which is believed greatly superior to die casing machines of conventional construction employing tie rods on which the traveling platen slides.

It has previously been mentioned that, when the traveling platen 20 is in rearward or outward position, the thrust rods or shafts 57 are received within the piston members 66. When the traveling platen 20 is moved forwardly by the screw shaft 49 to a position in which die 21 is about of an inch from die 22 the piston members 66 and thrust rods 57 will be spaced from one another a predetermined distance. In order that pressure may be exerted on the thrust rods 57 by the piston members 66, the block members 67 are moved from a position outward of the bores 66a in members 66, as shown in FIGURE 12, to a position sandwiched between the members 66 and 57, as shown in FIGURE 4. This movement of the blocks 67 occurs in a manner which will now be explained when the platen 20 has been moved forwardly by the screw 49 and the thrust rods 57 are suthciently forwardly to permit entrance of the blocks 67 between the rods 57 and members 66. A plate 148 mounting the ejector rods 149 which extend through passages 150 in the platen 20 and 151 in the die member 21 is provided between the side frame members or plates 14 between the fixed end plate member or abutment wall 11 and the reciprocating platen 20, as shown in FIGURES 4, 5, and 9. The front ends of piston members 66, which are of enlarged diameter as shown in FIGURE 10, are formed with vertically disposed grooves or passages 152 therein, for admitting the blocks 67.

3 Sheets-Sheet 3 Each member 66 has a pair of sldc llangcs 6611 against which clamping mcmbcrs 153 boar to secure the piston member 66 t the plate 148, suitable screws or bolts 154 connecting the members 153 and plate 148 and thereby the piston members 66 and plate 148 {or longitudinal movement, as shown. The plates 67 are of such thickness, relative to thc length of thc portions 152. as to provide the necessary clearance [or movement of blocks 67.

Plate 148 has an opening 156 freely passing the nut mcmbcr 47 and openings 157 which trccly pass the thrust rods 57. The blocks 67 are conncctcd at each sidc by vertically extending, rigid straps 158, as shown in FIGURES 9 and 10, the straps 158 bcing suitably secured to the blocks 67 by rivets or the like 159. The straps 158 at thc.right side of plate 148 in FIGURE 9 extend above thc uppcr block membcr 67 and are connected by a bar 160, as shown. Lugs 161 provided on the bar and on the top of the uppermost block 67 at the left side. of plate 148 in FlGURE 9 connect to link members 162 which suspcnd the system from an actuator member 163 which is automatically opcratcd upon movement of the yoke 112 to operate piston asscmbliss 59 in a manner which will be later described. Thc links 162 are pivotally connected to the lugs 161 and extending arms 163a of the actuator 163 by pins 164, as shown. As indicatcd in FIGURES 5 and 9, the actuator member 163 is pivotally mounted on plate 148 as at 164 and has a spherical shapcd, upper end 165 rcccivcd, as shown, within a clcvis 166 (FIGURES 9 and 11) on tho onc end of a rod mcmber 167. [n FIGURE 9 the actuator 163 is disposed such that blocks 67 are in alignment with thrust rods 57 in a position to permit the piston members 66 to apply prcssurc to the rods 57. If thc actuator member 163 is oppositely tilted, however, about its pivot 164, the left hand blocks 67 (FIGURE 9) will be raised to the position in which they are shown in FIGURE 12, out of the path of thrust rods 57 and the right hand blocks 67 will be lowcrcd the same distance so that they also are out of the path of thrust rods 57. Rctracting movement of the yoke 112, which adjusts the position of the actuator 163 to move the blocks 67 out of thc path of the thrust rods 57, will free the bores 66a of piston members 66 for entry of the rods 57 on the rctraction stroke of platcn 20.

The mechanism for automatically operating the actuator 163 will b: ncxt described, and attcntion is directed particularly to FIGURES 4, 9, and 11 [or a disclosurc thereof. The fixed wall 19 mounts a fixcd clcvis 168 under cylinder 126 and a clcvis pin 169 supports a sleeve 170 for swinging movement in a horizontal plane. Fixed on the member 170 which is provided with a front bearing 170a is a cam or track member generally dosignatcd 171 and having a trackway 172 with an angularly dircctcd portion 1720. Front and rear clamp members 173 are employed to fix the. track member 171 in position on tho tube 170. Mounted on the underside of cross head or connecting yoke member 112 by bolts or screws 174 is a plate 175 carrying a depcndcnt roller 176 which rides in the cam track 172. The tubular member 170 tclcscopically rcccivcs the rod 167 and when the roller 176 roaches thc portion 1724: of the track 172 it will necessarily pivot thc slccvc 170 and rod 167 about the pin 169. This, of coursc, has the died of changing the position of the actuator 163 about its ccntral pivot point 164. The plate 177, which is mounted on the upper edge of the plate 148 by screws 178 or the like, supports the outcr end of the rod 167 and is slotted as at 179 to pcrmit free movement of the upper end of the actuator member 163. If the position of piston mcm bcrs 66 is adjusted axially relative to member 64, as in a case where a die 21 or 22 having a different thickness is being substituted for the die in the machine, the rod 167 is free to move. axially in the tube or slccvc 170 to adjust to thc new position.

The die members 21 and 22 arc rclcasably secured to the movable platen 20 and fixed platen or frame mcmher 12 in any suitable manna-r. In the drawings, T-slols 180 are shown as provided in the members 20 and 12 to receive T nuts [81 which arc threaded on screws 182 carried by the dic mcmbcrs. In the case of the die 21, the die face is provided with cnlargcd openings 183 at points pcrlphcrally spaced from the die cavity 184 to receive the heads 185 of scrcws 182. The T slots which are not used in the drawings may be employed with other dics providing that the openings 1820 leading through the die members 21 and 12 are outside and spaced from tho dic cavity 184. As previously noted, the zicclor rods 149 arc carried by plate 148 and cxtcnd through to a position in which they are flush with the surface of the die cavity 184. During thc retract stroke of platen 20 when the piston members 66 are moved rearwardly initially by the piston return springs 75, the ejector pins 149 will movc the slight distance rearwardly with them. However, when the platen 20 is rapid traversed rcarwardly by the screw shaft 49 the pins 149 will opct'ate to strip the casting from the mold cavity so that it is t'rcc to fall to a suitable conveyor or the like positioned undcr the machine. Sincc the machine is supported on blocks 10 at its corncrs only, ample spacc is provided so that an endless convcyor may extend under the machine to convey the castings which are formcd in the machine on a quantity production schedule. When the position of piston members 66 is being adjusted and the screws 1S4 holding clamp plate 153 are backed off slightly to permit rotation of the piston members 66, the pins 186 projecting outwardly from plate 148 assist in supporting the plate 148 in position.

The Shot Infection System The charge of metal is applied to the die cavity 184 in a novel manner disclosed in applicant's copcnding application Serial No. 66,452. Prcfcrably, as previously notcd, a shot injection plunger 187 is cmploycd which moves at a relatively slow ratc of speed initially to close off a material supply spout, thence at a great rate of spccd, and with tremendous force, to movc the molten mctal or the like into thc dic cavity 184, and finally at a rclativcly reduced rate of spccd while retracting to original position. A longitudinally disposed, rectilinear housing 188 supportcd at one end by the wall 12 and at the other end by an upright housing or casing 189 is provided to house the shot plunger 187 which has an enlarged crtd 187a and is adapted to cxtcnd through an opening or cold chamber 190 in fixed die 22 and an aligned opening or cold chamber 191 through wall 12. The housing 188, which includes side walls 192 and a partial top wall 193, has integral sidc flanges 194 so that it can be scoured to the end wall 12 by bolt members 195.

It will be seen that the passages 190 and 191 are of tho diameter of the cnlargcd head 1870 of the, injection rod or plunger 187 and mountcd on the rear wall 12 is a member 196 having a bore 197 of the sam: diameter as openings 190 and 191. A pouring spout 198 leads through the member 196 from the exterior thereof to the bore 197 and, if it be assumed that thc top wall 193 terminates short 0! thc wall 12, than thc pouring spout 198 is exposed so that it may be manually or mechanically charged with the material to be formed in the dies.

The Control System and Operation At the beginning of the cycle when platen 20 and rctractablc die 21 are in rearward or retracted position and rack 201 and slidc 199 are also in retracted position. thc operator, in putting the systcm into operation, first of all must start the rapid traverse motor 37 and this can be dono by dcprcssing a push button 285 (FIGURE 13) to start the operation of the control system. The control 

1. IN A DIE CASTING OR MOLDING MACHINE; FRAME MEANS INCLUDING A FIXED WALL SECTION; A DIE NORMALLY FIXED ON SAID FRAME MEANS AT A SPACED DISTANCE FROM SAID WALL SECTION; A MOVABLE DIE ASSEMBLY BETWEEN SAID WALL SECTION AND DIE SUPPORTED BY SAID FRAME MEANS FOR RECIPROCATING MOVEMENT THEREBETWEEN; MEANS INCLUDING A ROTATABLE PART AND A GENERALLY RECIPROCABLE PART CONNECTED TO TRAVEL SAID MOVABLE DIE ASSEMBLY RAPIDLY TOWARD AND AWAY FROM SAID NORMALLY FIXED DIE; LOST MOTION COUPLING MEANS CONNECTING SAID LAST MEANS WITH THE SAID MOVABLE DIE ASSEMBLY PERMITTING SAID MOVABLE DIE ASSEMBLY A CLOSING INCREMENT OF MOVEMENT; MEANS FOR SUPPLYING SAID FIXED DIE WITH THE MATERIAL TO BE FORMED; A PLURALITY OF GENERALLY RADIALLY ARRANGED MEMBERS CARRIED BY SAID WALL SECTION FOR APPLYING A UNIFORM CLOSING PRESSURE TO SAID MOVABLE DIE ASSEMBLY AND MOVING IT A CLOSING INCREMENT TOWARD SAID NORMALLY FIXED DIE; AND FLUID PRESSURE MEANS 